Hydraulic motor



P 1934. H. F. GORSUCH El AL 1,974,775

HYDRAULIC MOTOR Filed NOV. 8, 1930 3 Shee12s-$heet l A TTORNE Y.

Sept. 25, 1934. H. F. GORSUCH ET AL HYDRAULIC MOTOR 3 Sheets-Sheet 2Filed NOV. 8, 1930 ZMMM ATTORNEY.

Sept. 25, 1934- 'H.F. GORSUCH ET AL HYDRAULI C MOTOR Filed Nov. 8, 19303 Sheets-Sheet 3 Patented Sept. 25, 1934 HYDRAULIC MOTOR. Howard ForestGorsuch and Carl B. Dupre.

Mansfield, Ohio, Philip Dupre,

assignors of one-third to Mansfield, Ohio Application November 8, 1930,Serial No. 494,413

1 Claim.

This inventionis directed to an improvement in hydraulic motors of therotary type, wherein a self-contained unitary construction involving apump and a rotary element are selectively operated and controlled tocompel a power output particularly serviceable for numerous uses.

The invention is more particularly designed to construct a relativelysmall, compact and selfcontained unit structure, necessitating the useof a comparatively small amount of the hydraulic medium, and involving apump, preferably of the rotary type, a rotor operated through thepressure or hydraulic medium incident to the operation of the pump, anda single valve arranged for manual control and adapted in that controlto utilize the power of the pump on the rotor, sustain the rotor in anyrelative fixed position under the pressure of the hydraulic medium, orrelieve the rotor of that pressure to permit the parts to assume anormal position, with the entire control functioning regardless of thecontinuous operation of the pump.

The invention is illustrated in the accompanying drawings, wherein:-

Figure 1 is a broken view in elevation illustrating the application ofthe motor for use in moving the body of a dump wagon, the body beingshown partly raised in full lines and fully raised in dotted lines.

Figure 2 is an enlarged elevation of the control valve of the motor.

Figure 3 is a section on the line 3--3 of Fig. 2.

Figure 4 is a vertical sectional view through the motor.

Figure 5 is a sectional view through the rotor.

Figure 6 is a perspective view of the rotor.

Figure '7 is a vertical sectional view through the motor, the line ofsection being at right angles to that shown in Figure 4.

Figure 8 is a bottom plan view of the motor.

The improved motor comprises a unit casting formed at one end to providea hollow rotor casing and at the opposite end to provide a relativelyoffset pump casing, the casting being also formed to provide a valvecasing for the reception of a valve, with the necessary ports andchannels of communication between the rotor casing, valve casing andpump being cored in or otherwise formed directly as an integralstructure with the unit casting.

In the preferred embodiment of specific detail as illustrated, the motorincludes a unit casting formed to provide a rotor casing 1, in the formof a hollow cylindrical body, the peripheral wall 2 of which is integralwith one side wall 3. The open end of the casing 1 opposite the sidewall 3 is designed to be closed by a cover 4 removably secured by bolts5 to a flange extension 6 of the peripheral wall 2 of the casing. Thewall 3 and cover 4 are formed with integral bearing extensions '7 inwhich is rotatably supported a power shaft 8, suitable packing glands 9being provided to prevent lubrication leakage.

A rotor 10 is mounted within the rotor casing, being keyed at 11 on thepower shaft 8. The rotor 10 has a diameter somewhat less than thesimilar dimension of the rotor casing and an axial length substantiallyequal to that of the rotor casing. A power vane 12 extends radially fromthe peripheral edge of the rotor, the free end of which vane is designedto provide a substantially non-leaking cooperation with the innersurface of the peripheral wall 2 of the rotor casing.

The peripheral wall 2 of the rotor casing 1 is interiorly provided withrelatively fixed abutments, that is, a pressure abutment 13 and a limitabutment 14. The pressure abutment 13 is arranged substantially at thelower end of the vertical diametric line of the casing, while the limitabutment is ofiset from this vertical line. As the power vane 12 movesfrom the pressure abutment 13 toward and into contact with the limitabutment 14 in a power stroke and does not move in the power directionbeyond the limit abutment 14, it will be apparent that the abutments 13and 14 divide the rotor casing into two chambers, that within which thepower vane moves, being hereafter referred to as the pressure chamber15, and that between the abutments 13 and 14 beyond the path of movementof the power vane being referred to as a reservoir 16.

In order that the inner surface of the peripheral wall of the rotorcasing can be accurately and easily machined to insure a non-leakingcooperation of the power vane therewith, it is preferred that thepressure abutment 13 and the limit abutment 14 be removably engaged withthis wall, for which purpose the wall at the appropriate points isprovided with an undercut channel 17 and the respective abutments formedwith corresponding projections 18 to slidably seat in the channel. Thusthe abutments, while having the capability of convenient removal, may beplaced in position after the machining of the peripheral wall of therotor casing and held against longitudinal movement by the fixed wall 3of the casing and the cover 4.

In providing sealing means for the rotor proper, the side walls of suchrotor, preferably adjacent the peripheral edge, are formed with annularchannels 19, which at determinate points circumferentially of the rotorare in communication through bores 21 of small diameter. Sealing rings22, having their outer surfaces machined for accurate sealing contactwith the walls of the rotor casing, seat in the respective channels 20,while coiled springs 23 of the compression type are seated in the bores21 and bear at the respective ends against the rings 22. These sealingrings are, therefore, held as compensating pressure in sealing contactwith the respective walls of the rotor casing, the arrangementfacilitating the removal or replacement of the rings or springs in asimple, convenient manner when necessary.

The power vane 12 and the pressure abutment 13 are formed at their freeend edges with sealing means to cooperate respectively with theperipheral wall of the rotor casing and with the peripheral surface ofthe rotor. The sealing means in these instances is identical, involvinga bar 24 seating in a recess 25 formed in the free end of the particularelement, pressure springs 26 being seated in shallow depth recesses 27formed in the element to exert an outward influence on the respectivesealing bars. The outer surfaces of the bars are accurately machined tocorrespond with and fit the curvature of the respective parts with whichthey oooperate, and the springs serve to maintain a sealing contact ofthe bar and, therefore, of the element in which the bar is mounted withrespect to the surface relative to which it is movin The integralcasting of the unit construction is formed below and preferablylaterally offset with respect to the rotor casing and with the body 28in which are formed the pump casing, the valve casing and the variouschannels for the flow of the hydraulic medium. This body is cored in adirection at right angles to the plane of the axial line of the rotor,with vertically aligned circular openings 29 and 30, in which aremounted cooperating gear bodies 31 and 32 intermeshing to form aconventional gear pump. The openings for the gears do not extend in onedirection entirely through the body, providing end extensions 33 inwhich one end of the shafts 34 of the respective gears may be mounted.The opposite end of the openings are closed by a removable cover plate35 formed to provide a bearing for the opposite end of the shaft of onegear, the shaft of the other gear being extended through its hearing at36 and connected to any suitable conventional or requiredinstrumentalities, with a conventional take-off from the power shaft ofthe motor of the vehicle. This detail is not illustrated, as it iscontemplated that any convenient means may be provided for selectivelyoperating the pump from the power of the vehicle motor and any and allnecessary details for such drive are to be included within the spirit ofthis invention. The primary object is the continuous operation of thepump after connection with the take-off is had, which, of course, is aselective one, in order that the hydraulic medium may be delivered underpressure from the pump for the operation of the power vane of the rotor.

In order that the rotor may be controlled, particularly in theapplication of the hydraulic motor with a dump body proper, it isessential that this control provide for several operations or conditionsof the rotor. That is to say, there must be a power operation in whichthe rotor is moved from the pressure abutment into contact with thelimit abutment, during which operation the dump body is elevated to thedesired inclination. Following this operation of the dump body, therotor must be held under the pressure of the hydraulic medium in itsthen position to permit the load to be discharged by gravity from theinclined dump body. Following the discharge of the load, or at otherselected interval, the power medium must be controlled to permit thedump body to return to normal position, this movement being accomplishedby relieving the pressure on the rotor and utilizing the weight of thebody to restore the parts to normal position. 0b viously, as the dumpbody is of considerable weight, this return movement should be more orless cushioned in order to avoid undue noise and An importantcharacteristic of the present invention is the means by which thiscontrol is provided, such means involving a single manually operablevalve capable in its various positions of permitting and maintaining thenecessary conditions and operations of the rotor to insure the desiredrelations of the dump body. The valve proper, indicated at 37, is ofslight conical form and designed to be rotatively mounted in a casingformed by an appropriate coring 38 in the body 28. The valve casingopens through the lower end of the body and the valve proper has areduced extension 39 providing an annular shoulder 40 at the lower endof the valve which bears against a wear plate 41 held by a cover plate42 removably secured to the body, this wear plate and cover plate beingformed with an opening to permit the passage of the extension 39therethrough, while at the same time holding the valve proper rotativelyin its casing 38. The valve 37 is formed at its upper end with atransverse channel 43 and near its lower end with a transverse channel44 having a right angled communicating channel 45 leading to and throughthe periphery of the valve, a semi-annular channel 46 in the surface ofthe valve providing communication between the respective ends of thechannels 44 and 45 inwardly of the surface of the valve proper.

In order to provide for the control of the rotor by the hydraulic mediumunder pressure in the operation of the pump, the rotor casing and valveports are arranged for control communication through the medium ofchannels cored or otherwise formed in the body 28. The body 28 is thusformed with what may be termed a. pressure channel 47 which opens intothe rotor casing immediately adjacent the pressure abutment 13 andbetween such abutment and the power vane when the latter is ininoperative or normal position, that is, with its rotor connected end incontact with the rotor contact end of the pressure abutment. Owing tothe relatively different inclinations radially of the power vane and thepressure abutment, the power vane when in normal position or in contactwith the pressure abutment presents a space between it and the pressureabutment on the peripheral wall of the rotor casing, into which spacethe pressure channel opens so that the hydraulic medium under pressurewill act at all times against the power vane. The pressure channel 47continues through the body in a plane including the plane of movement ofthe lower port 44 of the valve and continues beyond the valve casing, asat 49, to the pump and beyond the pump, as at 48, into the plane ofmovement of the upper port 43 of the valve.

A supply channel 50 formed in the body 28 opens into the reservoirchamber 16 of the rotor casing on the side of the pressure abutmentopposite that of the pressure channel and extends through the body intothe plane of the upper port 43 of the valve. The body 28 is furtherformed with a relief channel 52 which opens into the reservoir chamber16 of the rotor casing adjacent the supply channel and extends throughthe body into the plane of the lower ports 44 and A5 of the valve, thisrelief channel being extended at right angles to the similar end of thesupply channel 50.

With the valve set in the position shown in Figure 4, the hydraulicmedium, such as oil,'with which the rotor casing and channels are filledwill, by the operation of the pump, be drawn through the service channelfrom the reservoir 16, through the port 43 of the valve, through thepressure channel section 48, through the pump, through the pressurechannel 49, through the valve port 44, through channel 4'7 into therotor casing. The pressure of this medium under the action of the pumpresisted by the pressure abutment l3 acts to move the power vane 12 andthereby the rotor until the latter contacts with the limit abutment 14,it being apparent that the oil withdrawn from the reservoir by theaction of the pump and forced into the pressure chamber is incirculation as the oil ahead of the power vane is carried in themovement of that vane into the reservoir. After the rotor has been movedto its limit position, the valve 37 is slightly turned to cut offcommunication between the service channel 50 and the pump intake channel48.

By reason of the vertical oifsetting of the service ends of the upperand lower ports, this movement of the valve will cut off the servicechannel connection slightly before completely interrupting communicationbetween the sections 49 and 4'7 of the power channel. Thus the pump,which, of course, continues in operation, will force additional oil orat least create additional pressure in the rotor casing withoutwithdrawing oil from the reservoir, that is, the pump will step up thepressure so that as the valve is turned to finally cut off communicationbetween the sections 50 and 48 of the supply channel, the power vane,and thereby the rotor, will be held in operative position, with thepower vane against the limit abutment 14. This represents the dumpingposition of the dump body, as will later appear.

After the dumping operation or at any desired interval, the valve isfurther rotated to arrange the port 44 in position to establishcommunication between the valve ends of the pressure channel 47 andrelief channel 52. As these channels communicate respectively with thepressure chamber and with the reservoir of the rotor casing, it isapparent that a by-pass circulation is established between the pressurechamber and reservoir through the valve, and as the oil in the pressurechamber is thus relieved of its pressure, the weight of the dump bodytends to return the power vane to normal or inoperative position. Inthis movement, the oil in the pressure chamber behind the power vane isdelivered through the channel 47, valve port 44 and channel 52 to thereservoir, permitting the rotor to move to normal or inoperativeposition, cushioned by the gradual displacement of the oil from thepressure chamber.

In order to provide for necessary relief of the pressure flow of thehydraulic medium as the power vane reaches its limit position in contactwith the limit abutment 14, the rotor casing is provided with an ofiset53 in which is formed a bypass channel 54 opening into the rotor casingon the respective sides of the limit abutment 14. Thus when the powervane reaches the limit abutment under the continued pressure operationof the pump, the oil forced by this pressure into the pressure chamberwill by-pass around the power vane into the reservoir to maintain thecirculation necessary to avoid breakage of parts or cessation ofmovement of the pump under resistances of extreme pressure.

As the limit abutment 14 is primarily to limit operative position of thepower vane, this abutment need not contact with the rotor 10 and,therefore, is preferably of restricted projection inwardly of theperipheral wall of the rotor casing, as indicated in Figure 'l of thedrawings. To facilitate charging of the system with the hydraulic mediumand also to provide for the escape of accumulated air, a pipe section 55is provided which, through a suitable elbow connection 56, opens intothe reservoir of the rotor casing. This pipe connection is terminallyprovided with a ball valve 5'? opening under pressure from within therotor casing and provided with a cap 58 having air vents 59 and means,such as a spring 60, to insure the seating of the valve in the absenceof operating pressure.

The power shaft 8 extends in both directions beyond the rotor casing andis provided on each end with a removable, relatively fixed arm 61connected by links 62 to a conventional dump body 63 swingingly suportedat 64 on a chassis 65. Obviously, in the rotation of the power shaft 8,the arms 61 are operated and through the links the dump body is swung onits pivotal mounting to the desired inclination for dumping purposes. Ofcourse, the arms 61 and links 62 may be of such relative size as tosecure practically any desired inclination of the dump body during theoperative movement of the rotor, and as the arm and link are duplicatedat the respective ends of the power shaft, the power applied to the dumpbody is at transversely separated points to insure uniform movement ofthe body.

The valve projection 39 is provided with an operating arm 66 preferablypinned thereto and designed to be connected by a rod (not shown) to asuitable lever (not shown) arranged in the cab in a position convenientto the driver so that the various operations of the valve may be readilyand easily carried out.

We claim:--

A hydraulic motor unit including an integral casting formed to provide arotor casing and a pump casing, a rotor operative in the rotor casing,the rotor and rotor casing providing a pressure chamber and a reservoir,a pump operative in the pump casing, the pump casing being formed with asupply channel opening into the reservoir of the rotor casing andleading through the pump casing to one side of the pump and a pressurechannel leading from the opposite side of the pump through the pumpcasing and opening into the pressure chamber of the rotor casing, arelief channel opening from the reservoir of the rotor casing andleading into the pressure channel, a valve having an upper port tocontrol the supply channel between the intake side of the pump and therotor casing, and a lower port to control the pressure channel betweenthe discharge side of the pump and the rotor casing, the lower port ofthe valve controlling communication between the relief channel and thatportion of the pressure channel between such lower port of the valve andthe rotor casing, the valve operating in one movement to simultaneouslycut off the communication 3 [r.. 5.] IL. s.]

